WO2001053693A2 - Soupape de regulation de liquides - Google Patents

Soupape de regulation de liquides Download PDF

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Publication number
WO2001053693A2
WO2001053693A2 PCT/DE2000/004172 DE0004172W WO0153693A2 WO 2001053693 A2 WO2001053693 A2 WO 2001053693A2 DE 0004172 W DE0004172 W DE 0004172W WO 0153693 A2 WO0153693 A2 WO 0153693A2
Authority
WO
WIPO (PCT)
Prior art keywords
valve
injection
unit
control voltage
valve according
Prior art date
Application number
PCT/DE2000/004172
Other languages
German (de)
English (en)
Other versions
WO2001053693A3 (fr
Inventor
Johannes-Jörg Rueger
Patrick Mattes
Wolfgang Stoecklein
Udo Schulz
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP00988644A priority Critical patent/EP1185787B1/fr
Priority to US09/937,159 priority patent/US6705544B1/en
Priority to DE50010174T priority patent/DE50010174D1/de
Publication of WO2001053693A2 publication Critical patent/WO2001053693A2/fr
Publication of WO2001053693A3 publication Critical patent/WO2001053693A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/004—Actuating devices; Operating means; Releasing devices actuated by piezoelectric means
    • F16K31/007—Piezoelectric stacks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
    • F02D2041/2051—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using voltage control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F02D2041/224—Diagnosis of the fuel system
    • F02D2041/225—Leakage detection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0602—Fuel pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F02D41/402—Multiple injections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention is based on a valve for controlling liquids according to the type defined in more detail in the preamble of claim 1.
  • Such a valve is described in DE 197 328 02 for a fuel injection device of an internal combustion engine with a high-pressure system (common rail system).
  • This fuel injection device has two valve seats, which interact with sealing surfaces of a valve closing member when actuated by a piezo drive in a movement sequence, the valve closing member being initially in the closed position on the first valve seat, then being brought into an intermediate position between the valve seats and then again in a closed position to get to the second valve seat.
  • a piezoelectric actuator is charged to a rail-dependent voltage, which lengthens the actuator and the resulting movement of the valve closing. links to the second valve seat. The actuator is discharged to reverse the valve closing member in the direction of the first valve seat.
  • valve closing member The movement of the valve closing member from one valve seat to the other provides a brief relief for a valve control chamber under high pressure, the pressure level of which determines an open or closed position of a valve needle in the force-balanced fuel injection device and thus controls the fuel injection.
  • the fuel injection is made possible while the valve closing member is in an intermediate position between the two valve seats. In this way, double fuel injection, e.g. a pre-injection and a main injection can be realized by means of a single excitation of the piezo drive.
  • the pressure build-up in the hydraulic chamber which acts as a hydraulic coupler, is decisive for the stroke length of the valve member. If the piezoelectric actuator is acted upon so strongly with voltage that the valve closing member moves out of its valve seat, part of the amount of fuel in the hydraulic chamber is pressed out through its leakage gaps. This effect is particularly great if the control valve is held on the second valve seat facing the high-pressure region, since in this case the counterforce is particularly large due to the rail pressure.
  • the refilling of the low pressure area or the Hydraulic coupler is carried out by a system pressure, which can be 15 bar in practice, for example, via this leakage gap, but only during the time during which the actuating actuator is not activated.
  • valves known from practice which are equipped with only one valve seat, the valve closing member being lifted out of this valve seat and moved back again.
  • valve according to the invention for controlling liquids with the features of patent claim 1 has the advantage that the valve lift can be carried out identically for all injections by means of a correspondingly modified control voltage of the piezoelectric unit. In this way it is possible, even with a high pressure level in the high pressure range, to carry out short successive injections, as may be necessary in the case of pre-injection, main injection and post-injection, to improve the consumption and exhaust gas values, with reproducible stroke lengths for all injections F, since this varies of the low-pressure region or the hydraulic coupler, which represents the hydraulic chamber, can be compensated for via the control voltage.
  • valve according to the invention in which, in addition to taking into account the pressure level in the high pressure range, a modification of the control voltage as a function of leakage losses and refilling, is carried out, a stable injection can advantageously be guaranteed.
  • an actuation duration of a previous injection is output to the electrical actuation unit.
  • the actuation duration of the previous injection represents a reliable quantity for the amount of hydraulic fluid which was pressed out via leakage points during the loading time of the hydraulic coupler.
  • it can be provided as a very reliable value for the refilling of the low pressure area that a time interval between an end of the previous injection and the beginning of the subsequent injection is output to the electrical control unit, since this The time interval generally corresponds to the refill time. The degree of filling of the coupler before the subsequent injection can thus be determined from the refilling time and loading time.
  • FIG. 1 shows a schematic, partial illustration of an exemplary embodiment of the invention in the case of a fuel injection valve for internal combustion engines in a longitudinal section;
  • FIG. 2 shows a signal flow block diagram with a characteristic map of an electrical control unit for correcting the control voltage of the piezoelectric unit of the fuel injection valve according to FIG. 1.
  • FIG. 1 shows a use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • the fuel injection valve 1 is designed here as a common rail injector, the fuel injection being controlled via the pressure level in a valve control chamber 2, which is connected to a high-pressure supply.
  • a valve element 3 is controlled via a piezoelectric unit designed with a piezoelectric actuator 4, which is arranged on the side of the valve member 3 facing away from the valve control chamber and combustion chamber.
  • the piezoelectric actuator 4 is constructed in a known manner from several layers and has an actuator head 5 on its side facing the valve member 3 and an actuator foot 6 on its side facing away from the valve member 3, which is supported on a valve body 7.
  • An actuator piston 9 of the valve member 3 bears on the actuator head 5 via a support 8, the piston being designed in stepped diameter.
  • valve member 3 which can be actuated via the piezoelectric actuator 4, is arranged axially displaceably in a bore 13 which is designed as a longitudinal bore and is designed in a multiple manner, wherein in addition to the actuating piston 9 it also has an actuating piston 14 which is provided for actuating a spherical valve closing member 15.
  • the stem piston 9 and the actuating piston 14 are coupled to one another by means of a hydraulic transmission.
  • the hydraulic transmission by means of which the deflection of the pi ⁇ zo ⁇ l ⁇ ktnsch ⁇ n actuator 4 is transmitted down to the valve closing member 15, represents a hydraulic chamber 16.
  • the hydraulic chamber 16 closes between the two pistons 9 and 14 which limit it, of which the actuating piston 14 has a smaller one Diameter as the steep piston 9 is formed, a common compensation volume.
  • the hydraulic chamber 16 is clamped between the actuating piston 9 and the actuating piston 14 in such a way that the actuating piston 14 increases the stroke by the ratio of the piston diameter when the larger actuating piston 9 is moved by the pi ⁇ zo ⁇ lectrical actuating path.
  • the piezoelectric actuator 4, the steep piston 9 and the actuating piston 14 lie one behind the other on a common axis.
  • the hydraulic chamber 16 also serves as a tolerance compensation element for elongation tolerances in the components of the fuel Spray valve 1 due to temperature gradients ⁇ n or different coefficients of thermal expansion of the materials used as well as for possible set effects.
  • the pistons 9 and 14 can be immersed in the volume of the hydraulic chamber 13 and withdrawn therefrom without thereby causing a change in the position of the valve closing member 15 to be actuated.
  • valve closing gate 15 interacts with two valve seats 18, 19 formed on the valve body 7.
  • the first or upper valve seat 18 limits its low pressure range 20, while the second or lower valve seat 19 leads to the valve control chamber 2, which is assigned to a high pressure region 21.
  • the second valve seat 19 is assigned spring 28, which holds the valve closing member 15 on the first valve seat 18 when the valve control chamber is relieved.
  • a movable valve control piston is arranged in the valve control chamber 2 of the high-pressure area 21 and is not shown in the drawing.
  • An injection nozzle of the fuel injection valve 1 is controlled in a manner known per se by axial movements of the valve control piston in the valve control chamber 2.
  • An injection line, which supplies the injection nozzle with fuel, also usually opens into the valve control chamber 2.
  • the injection line is connected to a common high-pressure storage chamber (common rail) for several fuel injection valves.
  • the high-pressure storage space is known from a high-pressure fuel delivery pump fed with high pressure fuel from ⁇ in ⁇ m storage tank.
  • a valve system pressure chamber 22 connects to the pi ⁇ zcs ⁇ itig ⁇ end of the bore 13. This is limited on the one hand by the valve body 7 and on the other hand by sealing element 23 connected to the valve piston 9 of the valve member 3 and the valve body 7, which in the present case is designed as a bellows-type membrane and prevents the piezoelectric fuel system 4 containing the valve actuator 22 contained in the valve chamber 22 comes into contact.
  • a leakage amount of the low pressure area 20 can be compensated by removing hydraulic fluid from the high pressure area 21. This is done by the filling device 24, which opens into the valve system pressure chamber 22, which communicates with the hydraulic chamber 16 via the gap 25 surrounding the steep piston 9, so that the hydraulic chamber 16 can also be filled via the gap 25.
  • the filling device 24 opens into another system pressure chamber or directly into the gap 25 or into a gap 26 surrounding the actuating pistons 14.
  • the fuel injection valve 1 according to FIG. 1 works in the manner described below.
  • valve closing member 15 of the valve member 3 is held in contact with the upper valve seat 18 assigned to it, so that no fuel can get into the low pressure area 20 from the valve control chamber 2 connected to the high pressure storage area.
  • the adjusting piston 9 penetrates into the compensating volume of the hydraulic chamber 16 with an increase in temperature or withdraws therefrom when the temperature drops, without this having an effect on the closing and opening setting of the valve and the fuel 3 in its entirety.
  • the piezoelectric actuator 4 is energized, as a result of which its axial expansion increases abruptly. This elongation of the piezoelectric actuator 4 is transferred to the actuating piston 14 via the steep piston 9 and the hydraulic chamber 16, as a result of which the valve closing member 15 is lifted out of the first, upper valve seat 18 and is moved against the rail pressure applied against the second, lower valve seat 19 ,
  • the electrical control unit 12 not only detects the pressure level in the high-pressure region 21, ie the rail pressure, but also the loss of leakage in the low-pressure region 20 from the hydraulic chamber 16 during a previous one. Injection El and the re-filling are taken into account.
  • the electrical control unit 12 has a characteristic diagram 27 for this purpose, the input data being a control duration T_ ⁇ 1 of the previous injection El and a time interval T_E1 ⁇ 2 between the end of the previous injection El and the beginning of the subsequent injection ⁇ 2.
  • the activation time T_E1 of the previous injection El and the time interval T_E1E2 indicate the loss of leakage from the low pressure region 20 and the refilling time since the previous injection El.
  • a correction value of the control voltage ⁇ U is output, which is added to the basic value of the control voltage, which is mainly measured from the rail pressure.
  • the correction value .DELTA.U of the control voltage is dimensioned such that the control voltage increases with successive injections in order to compensate for a difference between the leakage loss and the heat filling of the low pressure range 20. In this way, a reproducible stroke length of the valve member 3 or actuating piston 14 is achieved and it is ensured that, on the one hand, a correct injection takes place and, on the other hand, the valve closing member 15 always comes into contact with the second valve seat 19.
  • the control of the piezoelectric unit is even more precise if the electronic control unit 12 additionally corrects the control voltage with respect to the current temperature of the piezoelectric actuator 4.
  • valve closing member 15 is stabilized in its central position. It can also be provided that the valve 1 does not work as a double-switching valve, but that the valve closing member only interacts with the first valve seat 18.
  • a control in which the valve closing member is moved into the second valve seat 19 at high speed and high voltage, so that the injection takes place during the return movement from the second valve seat 19 in the first valve seat 18, is also conceivable with the valve according to the invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

Soupape (1) de régulation de liquides qui comporte une unité piézo-électrique (4) destinée à actionner un élément (3) de soupape mobile axialement dans un alésage (13) du corps (7) de soupape. Ledit élément est constitué d'un piston de réglage (9) adjacent à l'unité (4) piézo-électrique et d'au moins un piston d'actionnement (14) adjacent à un obturateur (15) de soupape. Une chambre hydraulique (16) fonctionnant en tant que transmission hydraulique est située entre les pistons (9, 14). L'obturateur (15) de soupape coopère avec au moins un siège (18, 19) de soupape et sépare une zone à basse pression (20) d'une zone à haute pression (21). Une unité de commande électrique (21) fournit la tension d'excitation à l'unité piézo-électrique (4) en fonction du niveau de pression dans la zone à haute pression (21), d'une perte par fuite dans la zone à basse pression (20), en particulier dans la chambre hydraulique (16), et du remplissage renouvelé de la zone à basse pression.
PCT/DE2000/004172 2000-01-20 2000-11-24 Soupape de regulation de liquides WO2001053693A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP00988644A EP1185787B1 (fr) 2000-01-20 2000-11-24 Soupape de regulation de liquides
US09/937,159 US6705544B1 (en) 2000-01-20 2000-11-24 Valve for controlling liquids
DE50010174T DE50010174D1 (de) 2000-01-20 2000-11-24 Ventil zum steuern von flüssigkeiten

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10002270A DE10002270C1 (de) 2000-01-20 2000-01-20 Ventil zum Steuern von Flüssigkeiten
DE10002270.7 2000-01-20

Publications (2)

Publication Number Publication Date
WO2001053693A2 true WO2001053693A2 (fr) 2001-07-26
WO2001053693A3 WO2001053693A3 (fr) 2001-12-27

Family

ID=7628116

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2000/004172 WO2001053693A2 (fr) 2000-01-20 2000-11-24 Soupape de regulation de liquides

Country Status (5)

Country Link
US (1) US6705544B1 (fr)
EP (1) EP1185787B1 (fr)
KR (1) KR100717525B1 (fr)
DE (2) DE10002270C1 (fr)
WO (1) WO2001053693A2 (fr)

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Publication number Priority date Publication date Assignee Title
EP1424492A2 (fr) 2002-11-26 2004-06-02 Robert Bosch Gmbh Vanne de commande de liquides avec une buse et une valve de commande

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DE10032022B4 (de) * 2000-07-01 2009-12-24 Robert Bosch Gmbh Verfahren zur Bestimmung der Ansteuerspannung für ein Einspritzentil mit einem piezoelektrischen Aktor
DE10112147A1 (de) * 2001-03-14 2002-09-19 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10123173A1 (de) * 2001-05-12 2002-11-14 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10136186A1 (de) * 2001-07-25 2003-02-06 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10155391A1 (de) * 2001-11-10 2003-05-22 Bosch Gmbh Robert Verfahren zum Laden und Entladen eines piezoelektrischen Elementes
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DE10162045B4 (de) 2001-12-17 2005-06-23 Siemens Ag Vorrichtung zum Übersetzen einer Auslenkung eines Aktors, insbesondere für ein Einspritzventil
DE10321999A1 (de) * 2002-07-31 2004-02-12 Robert Bosch Gmbh Verfahren und Vorrichtung zur Ansteuerung eines Aktors
DE10239614A1 (de) * 2002-08-29 2004-03-11 Robert Bosch Gmbh Verfahren zum Betreiben eines Kraftstoffeinspritzsystems, Computerprogramm sowie Steuer- und/oder Regelgerät zum Betreiben eines Kraftstoffeinspritzsystems und Brennkraftmaschine
DE10254844A1 (de) 2002-11-25 2004-06-03 Robert Bosch Gmbh Verfahren und Vorrichtung zum Betrieb eines Einspritzsystems einer Brennkraftmaschine
DE10305525B4 (de) * 2003-02-11 2014-04-24 Robert Bosch Gmbh Verfahren und Vorrichtung zur Adaption der Druckwellenkorrektur in einem Hochdruck-Einspritzsystem eines Kraftfahrzeuges im Fahrbetrieb
DE10317654B4 (de) 2003-04-17 2018-05-30 Robert Bosch Gmbh Verfahren und Vorrichtung zur driftkompensierenden Steuerung von Injektoren eines Kraftstoffzumesssystems einer Brennkraftmaschine
DE10323488B4 (de) * 2003-05-23 2011-08-11 Robert Bosch GmbH, 70469 Verfahren und Vorrichtung zur betriebspunktabhängigen Steuerung von Injektoren eines Kraftstoffzumesssystems einer Brennkraftmaschine
DE10331241B4 (de) * 2003-07-10 2014-04-30 Robert Bosch Gmbh Verfahren zum Injektormengenabgleich (IMA) bei Voreinspritzungen in einem Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE10336639A1 (de) * 2003-08-08 2005-03-03 Robert Bosch Gmbh Verfahren und Vorrichtung zur Funktionsdiagnose eines Piezoaktors eines Kraftstoffzumesssystems einer Brennkraftmaschine
DE10343759B4 (de) * 2003-09-22 2015-01-15 Robert Bosch Gmbh Verfahren und Vorrichtung zur Bestimmung der Abweichung der tatsächlichen Einspritzmenge von einer berechneten Referenzeinspritzmenge eines Kraftstoffeinspritzsystems
DE102004053418B4 (de) * 2004-03-24 2016-05-04 Robert Bosch Gmbh Verfahren und Vorrichtung zur druckwellenkompensierenden Steuerung zeitlich aufeinanderfolgender Einspritzungen in einem Einspritzsystem einer Brennkraftmaschine
DE102005036192A1 (de) 2005-08-02 2007-02-08 Robert Bosch Gmbh Verfahren zur Steuerung eines Einspritzsystems einer Brennkraftmaschine
DE102005036190A1 (de) * 2005-08-02 2007-02-08 Robert Bosch Gmbh Verfahren und Vorrichtung zur Steuerung eines Einspritzsystems einer Brennkraftmaschine
DE102007009565A1 (de) 2007-02-27 2008-08-28 Robert Bosch Gmbh Verfahren und Vorrichtung zur Bestimmung der Kraftstoffzusammensetzung in einem Einspritzsystem einer Brennkraftmaschine, insbesondere eines Kraftfahrzeugs
DE102012204216A1 (de) * 2012-03-16 2013-09-19 Robert Bosch Gmbh Baugruppe
DE102013204103A1 (de) * 2013-03-11 2014-09-11 Robert Bosch Gmbh Verfahren zum Ansteuern eines Einspritzventils
DE102015220405A1 (de) 2015-10-20 2017-04-20 Robert Bosch Gmbh Verfahren und Vorrichtung zur Steuerung eines Kraftstoff-Einspritzsystems einer Brennkraftmaschine
DE102016214266A1 (de) 2016-08-02 2018-02-08 Robert Bosch Gmbh Verfahren zur Kompensation einer Temperaturabhängigkeit eines hydraulischen Kopplers
CN112170105B (zh) * 2020-09-18 2022-06-10 深圳市轴心压电技术有限公司 一种新型压电陶瓷阀驱动控制系统

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KR100717525B1 (ko) 2007-05-14
EP1185787A2 (fr) 2002-03-13
DE50010174D1 (de) 2005-06-02
DE10002270C1 (de) 2001-06-28
EP1185787B1 (fr) 2005-04-27
US6705544B1 (en) 2004-03-16
KR20010113850A (ko) 2001-12-28
WO2001053693A3 (fr) 2001-12-27

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